JP6432768B2 - Waste heat recovery device, heating system, steam boiler and deodorization system - Google Patents

Description

  The present disclosure relates to an exhaust heat recovery apparatus. The present disclosure also relates to a heating system, a steam boiler, and a deodorization system including the exhaust heat recovery device.

  Conventionally, as a means for effectively utilizing exhaust heat, a Rankine cycle that extracts work by a temperature difference between a high-temperature heat source having exhaust heat and a low-temperature heat source requiring preheating is known. For example, an exhaust heat recovery apparatus having a Rankine cycle that uses exhaust gas discharged from a vehicle combustion engine that uses combustible gas as a fuel as a high-temperature heat source, and uses a combustible gas that vaporizes from liquid fuel as a low-temperature heat source. Are known.

  Patent Document 1 describes an exhaust heat recovery apparatus 500 as shown in FIG. In the condenser 520, Rankine cycle working fluid (for example, Freon) is condensed by isobaric cooling using the heat of vaporization of the combustible gas supplied from the tank 516 to the combustion engine 510. The pump 532 adiabatically compresses the working fluid. The working fluid is heated at an equal pressure using the heat of the exhaust gas by heat exchange in the heat exchanger 514 to evaporate. The working fluid evaporated by the turbine 526 is adiabatically expanded to extract exhaust heat of the exhaust gas as work.

JP 2003-278598 A

The exhaust heat recovery apparatus described in Patent Document 1 has room for improvement from the viewpoint of improving the operation efficiency of the Rankine cycle and efficiently using the exhaust heat.
In view of the above circumstances, an exemplary embodiment that is not limited provides an exhaust heat recovery device that is more efficient in Rankine cycle operation and that can efficiently use exhaust heat.

  The present disclosure includes an exhaust heat channel for flowing a first heat medium having exhaust heat, a second heat medium channel for flowing a second heat medium having a temperature lower than the temperature of the first heat medium, and a pump The working fluid is evaporated by evaporating the working fluid by exchanging heat between the first heat medium and the working fluid flowing in the exhaust heat flow path in the evaporator, including an evaporator, an expander, and a condenser. A Rankine cycle in which a working fluid is expanded by the expander to generate power, and the first heat medium flowing through the exhaust heat flow path and the second heat medium flowing through the second heat medium flow path. An exhaust heat recovery apparatus comprising: an exhaust heat recovery heat exchanger for recovering exhaust heat of the first heat medium by heating the second heat medium by heat exchange.

  According to the present disclosure, it is possible to provide an exhaust heat recovery device that has higher Rankine cycle operation efficiency than the conventional one and can efficiently use exhaust heat.

Configuration diagram of exhaust heat recovery apparatus according to the first embodiment Configuration diagram of exhaust heat recovery apparatus according to the first modification Configuration diagram of exhaust heat recovery apparatus according to second modification Configuration diagram of exhaust heat recovery apparatus according to the third modification Configuration diagram of a heating system equipped with an exhaust heat recovery device Configuration diagram of a steam boiler with an exhaust heat recovery device Configuration diagram of deodorization system with exhaust heat recovery device Configuration diagram of deodorization system according to modification Configuration diagram of conventional waste heat recovery system

  When power is generated by the Rankine cycle, for example, when power is generated by the Rankine cycle, the power generation efficiency at the power generation end of the Rankine cycle is obtained by dividing the power generation output from the generator by the amount of heat recovered by the evaporator. When the high-temperature working fluid heated and evaporated by the evaporator flows to the condenser having a low pressure, the rotating mechanism in the expander or the turbine rotates to generate power (work). As a result, the generator is driven to generate power. That is, the greater the difference between the pressure of the working fluid in the evaporator and the pressure of the working fluid in the condenser, the greater the power output by the generator.

  The pressure of the working fluid in the evaporator and the pressure of the working fluid in the condenser are determined by the temperature at which the working fluid evaporates in the evaporator and the temperature at which the working fluid condenses in the condenser, respectively. The temperature at which the working fluid evaporates is affected by the lowest temperature of the hot heat source and the heat exchange performance of the evaporator. The temperature at which the working fluid condenses is affected by the highest temperature of the low temperature heat source and the heat exchange performance of the condenser. When exhaust heat of exhaust gas that is a high-temperature heat source is recovered only by the Rankine cycle as in the exhaust heat recovery apparatus 500 described in Patent Document 1, if the exhaust heat recovery amount in the heat exchanger 514 is increased, the heat recovery is performed. The temperature of the later exhaust gas decreases, and the temperature at which the working fluid evaporates decreases. For this reason, the difference between the pressure of the working fluid in the evaporator and the pressure of the working fluid in the condenser becomes small, and the power generation output becomes small. As a result, the conventional exhaust heat recovery apparatus may operate in a state where the efficiency of power generation by the Rankine cycle is low. On the other hand, if the temperature of the high-temperature heat source is too high, the power required for the Rankine cycle pump increases and the Rankine cycle efficiency decreases.

  Further, in the exhaust heat recovery apparatus 500 of Patent Document 1, if the exhaust gas temperature in the heat exchanger 514 is kept high, the amount of exhaust heat recovered by the exhaust gas is reduced, and the exhaust heat possessed by the exhaust gas is efficiently reduced. It becomes difficult to use.

  Further, in the conventional exhaust heat recovery apparatus, since all of the exhaust heat recovery is performed in the Rankine cycle, there is a problem that the amount of heat exchange with respect to the amount of power generation becomes large, the Rankine cycle becomes large, and cost reduction is difficult.

  A first aspect of the present disclosure includes an exhaust heat flow path for flowing a first heat medium having exhaust heat, and a second heat medium flow for flowing a second heat medium having a temperature lower than the temperature of the first heat medium. The working fluid is evaporated by exchanging heat between the first heat medium flowing through the exhaust heat flow path and the working fluid in the evaporator, and a path, a pump, an evaporator, an expander, and a condenser. A Rankine cycle in which the evaporated working fluid expands in the expander to generate power, and the second heat medium flow passes through the first heat medium flow and the second heat medium flow path. An exhaust heat recovery device comprising: an exhaust heat recovery heat exchanger for recovering exhaust heat of the first heat medium by heating the second heat medium by exchanging heat with the heat medium To do.

  According to the first aspect, the exhaust heat of the first heat medium is recovered by the exhaust heat recovery heat exchanger, and heat exchange is performed between the first heat medium and the working fluid in an appropriate temperature range as a high-temperature heat source in the evaporator. be able to. For this reason, the operation efficiency of the Rankine cycle is high. In addition, since the second heat medium can be heated by the exhaust heat of the first heat medium that is not recovered by the Rankine cycle, the exhaust heat of the first heat medium can be used efficiently. Since the amount of exhaust heat recovered by the Rankine cycle can be reduced, the Rankine cycle can be miniaturized and the cost can be reduced.

  According to a second aspect of the present disclosure, in the first aspect, the second heat medium flow path is configured to supply the second heat medium heated by the exhaust heat recovery heat exchanger to a predetermined heat process. An exhaust heat recovery device is provided. According to the second aspect, the second heat medium supplied to the predetermined heat process can be preheated by the exhaust heat of the first heat medium in the exhaust heat recovery heat exchanger.

  A third aspect of the present disclosure provides the exhaust heat recovery apparatus according to the first aspect or the second aspect, further including a generator that generates electric power using the power. According to the 3rd aspect, heat energy can be converted into electrical energy with large exergy.

  According to a fourth aspect of the present disclosure, in any one of the first aspect to the third aspect, the Rankine cycle is heated by the working fluid expanded by the expander and the exhaust heat recovery heat exchanger in the condenser. Provided is an exhaust heat recovery device that condenses the working fluid by exchanging heat with the second heat medium flowing through the second heat medium flow path before being performed. According to the fourth aspect, the working fluid can be condensed by the second heat medium before being heated by the exhaust heat recovery heat exchanger.

  According to a fifth aspect of the present disclosure, in the fourth aspect, the exhaust heat recovery heat exchanger includes the first heat medium flowing through the exhaust heat flow path after exchanging heat with the working fluid in the evaporator; Provided is an exhaust heat recovery apparatus for exchanging heat with the second heat medium flowing through the second heat medium flow path after heat exchange with the working fluid in the condenser. According to the fifth aspect, since the difference between the temperature of the first heat medium that is the high-temperature heat source in the evaporator and the temperature of the second heat medium that is the low-temperature heat source in the condenser is large, the power generation efficiency by the Rankine cycle is high. . Further, since the exhaust heat of the first heat medium after heat exchange with the working fluid in the evaporator can be recovered by the exhaust heat recovery heat exchanger, the exhaust heat of the first heat medium can be used efficiently.

  According to a sixth aspect of the present disclosure, in the fourth aspect, the exhaust heat recovery heat exchanger includes the first heat medium flowing through the exhaust heat flow path before exchanging heat with the working fluid in the evaporator; Provided is an exhaust heat recovery apparatus for exchanging heat with the second heat medium flowing through the second heat medium flow path after heat exchange with the working fluid in the condenser. According to the sixth aspect, when the temperature of the first heat medium is too high for the Rankine cycle, the temperature of the working fluid in the evaporator is appropriately lowered by heat exchange with the second heat medium in the exhaust heat recovery heat exchanger. be able to. Thereby, the temperature of the 1st heat carrier in an evaporator is settled in the temperature range which can operate Rankine cycle efficiently. Since the amount of exhaust heat recovered by the Rankine cycle can be reduced, the Rankine cycle can be reduced in size.

According to a seventh aspect of the present disclosure, in any one of the first aspect to the third aspect, the Rankine cycle includes a cooling medium that is different from the second heat medium and the working fluid that is expanded in the expander in the condenser. The first heat medium flowing through the exhaust heat flow path before heat exchange with the working fluid in the evaporator. And an exhaust heat recovery device that exchanges heat with the second heat medium flowing through the second heat medium flow path. According to the seventh aspect, when the temperature of the second heat medium is not appropriate as the temperature of the low temperature heat source of the Rankine cycle, the working fluid can be condensed in the condenser by the cooling medium different from the second heat medium. In addition, when the temperature of the first heat medium is too high for the Rankine cycle, the temperature of the working fluid in the evaporator can be appropriately reduced by heat exchange with the second heat medium in the exhaust heat recovery heat exchanger. As a result, the temperature of the first heat medium in the evaporator falls within the temperature range in which the Rankine cycle operates efficiently. In addition, since the amount of exhaust heat recovered by the Rankine cycle can be reduced, the Rankine cycle can be reduced in size.

  According to an eighth aspect of the present disclosure, in any one of the first aspect to the third aspect, the Rankine cycle includes a cooling medium that is different from the second heat medium and the working fluid that is expanded by the expander in the condenser. The first heat medium flowing through the exhaust heat flow path after exchanging heat with the working fluid in the evaporator. And an exhaust heat recovery device that exchanges heat with the second heat medium flowing through the second heat medium flow path. According to the eighth aspect, when the temperature of the second heat medium is not appropriate as the temperature of the low temperature heat source of the Rankine cycle, the working fluid can be condensed in the condenser by the cooling medium different from the second heat medium. Moreover, since the difference of the temperature of the 1st heat medium which is a high temperature heat source in an evaporator and the temperature of the cooling medium which is a low temperature heat source in a condenser is large, the production | generation efficiency of the power by Rankine cycle is high. Further, since the exhaust heat of the first heat medium after heat exchange with the working fluid in the evaporator can be recovered by the exhaust heat recovery heat exchanger, the exhaust heat of the first heat medium can be used efficiently.

  A ninth aspect of the present disclosure includes a combustion section, a heating space for heating an object to be heated using heat generated in the combustion section, and an exhaust passage for discharging exhaust gas generated in the heating space. And an intake passage for supplying outside air to the combustion section, and the exhaust heat recovery device according to any of the fifth to eighth aspects, wherein the exhaust gas is the first exhaust gas. The second heat medium flow path is connected to the exhaust flow path so as to be supplied as a heat medium to the exhaust heat flow path, and the outside air passes through the second heat medium flow path as the second heat medium. A heating system is provided that forms at least a portion of the intake flow path to be supplied to the combustion section.

  According to the ninth aspect, the exhaust heat of the exhaust gas generated in the heating space can be used to generate power, and the outside air supplied to the combustion unit can be preheated in the exhaust heat recovery device. Thereby, the fuel used in a combustion part can be saved.

  A tenth aspect of the present disclosure provides the heating system according to the ninth aspect, further including a reheat channel for supplying a part of the air in the heating space to the combustion unit. According to the 10th aspect, since a part of air in heating space is supplied to a combustion part, the fuel in a fuel part can be saved.

  An eleventh aspect of the present disclosure includes a combustor, a steam generator that evaporates the liquid by exchanging heat between the combustion gas generated in the combustor and the liquid, and the liquid generator for supplying the liquid to the steam generator. And a waste heat recovery device according to any one of the fifth to eighth aspects, wherein the exhaust heat flow path is configured such that the combustion gas after heat exchange with the liquid is performed in the steam generator. The second heat medium flow path is configured to flow through the exhaust heat flow path as a first heat medium, and the second heat medium has the liquid to be supplied to the steam generator as the second heat medium. Provided is a steam boiler that forms at least a part of the liquid supply flow path so as to be supplied to the steam generator via the flow path.

  According to the eleventh aspect, power can be generated using the exhaust heat of the heat medium after heat exchange with the steam generator, and the liquid to be supplied to the steam generator can be preheated. This saves fuel used in the combustor.

  A twelfth aspect of the present disclosure includes a combustion section for burning odorous substances, an exhaust passage for discharging exhaust gas generated by burning the odorous substances in the combustion section, and a process fluid for a predetermined thermal process. And a waste heat recovery device according to any one of the fifth aspect to the eighth aspect, wherein the exhaust heat flow path uses the exhaust gas as the first heat medium. The second heat medium flow path is connected to the exhaust flow path so as to be supplied to the predetermined heat process via the second heat medium flow path as the second heat medium. A deodorization system is provided that forms at least a portion of the process fluid flow path as provided.

  According to the twelfth aspect, power can be generated using exhaust heat of exhaust gas generated by burning odorous substances, and a process fluid supplied to a predetermined heat process can be preheated in the exhaust heat recovery apparatus.

  According to a thirteenth aspect of the present disclosure, in the twelfth aspect, the combustion unit includes a preheating unit that preheats the odorous substance, and a catalytic combustion unit that causes the preheated odorous substance to come into contact with a catalyst to perform catalytic combustion. Provide a deodorization system. According to the thirteenth aspect, the odorous substance can be burned using the catalytic combustion method.

  According to a fourteenth aspect of the present disclosure, in the twelfth aspect or the thirteenth aspect, after the odorous substance is adsorbed on an adsorbent, the odorous substance is desorbed from the adsorbent and the odorous substance is concentrated. A supply flow path for supplying the odorous substance concentrated in the concentration section to the combustion section, and as the predetermined thermal process, the process fluid passing through the second heat medium flow path is used as the predetermined heat process. Provided is a deodorization system that heats the adsorbent adsorbed with an odor substance to desorb the odor substance from the adsorbent. According to the fourteenth aspect, the odorous substance can be concentrated by desorbing the odorous substance adsorbed on the adsorbent of the concentrating part using the process fluid preheated in the exhaust heat recovery apparatus.

  Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. The following description relates to an example of the present disclosure, and the present disclosure is not limited thereto.

<Exhaust heat recovery device>
As shown in FIG. 1, the exhaust heat recovery apparatus 150 </ b> A according to the first embodiment includes an exhaust heat flow path 110, a second heat medium flow path 112, a Rankine cycle 155, and an exhaust heat recovery heat exchanger 156. The exhaust heat channel 110 is a channel for flowing the first heat medium having exhaust heat. The first heat medium is a high-temperature exhaust fluid such as exhaust gas, pressurized water, or oil generated by combustion. The second heat medium flow path 112 is a flow path for flowing a second heat medium having a temperature lower than the temperature of the first heat medium. The second heat medium is, for example, a gas such as outside air or a liquid such as water supplied from the outside of the exhaust heat recovery apparatus 150A.

  The Rankine cycle 155 includes a pump 151, an evaporator 152, an expander 153, and a condenser 154, and the pump 151, the evaporator 152, the expander 153, and the condenser 154 are connected by a pipe in this order. The working fluid circulates through the Rankine cycle 155. The Rankine cycle 155 evaporates the working fluid in the evaporator 152 by exchanging heat between the first heat medium flowing through the exhaust heat flow path 110 and the working fluid. That is, the first heat medium flowing through the exhaust heat flow path 110 is a high temperature heat source of the Rankine cycle 155. The evaporator 152 is, for example, a double tube heat exchanger, a plate heat exchanger, a finned tube heat exchanger, or a shell and tube heat exchanger. The evaporator 152 is arrange | positioned at the exhaust heat flow path 110, for example. The working fluid of Rankine cycle 155 is not particularly limited, and is, for example, water, alcohol, ammonia, hydrocarbon, or halocarbon.

  In the Rankine cycle 155, the evaporated working fluid is expanded by the expander 153 to generate power. The expander 153 includes a rotation mechanism. The expander 153 is, for example, a turbine or a positive displacement expander. Examples of positive displacement expanders include scroll expanders and rotary expanders. The exhaust heat recovery apparatus 150 </ b> A further includes a generator 170. The generator 170 is driven by the expander 153. The generator 170 is connected to the expander 153 by a shaft, for example. The generator 170 generates power using the power generated by the Rankine cycle 155. For this reason, heat energy can be converted into electrical energy with high exergy. The expander 153 and the generator 170 may be integrally configured so as to be accommodated in the same casing, or may be accommodated in separate casings.

  The exhaust heat recovery heat exchanger 156 heats the second heat medium by exchanging heat between the first heat medium flowing through the exhaust heat flow path 110 and the second heat medium flowing through the second heat medium flow path 112. And a heat exchanger for recovering the exhaust heat of the first heat medium. That is, the exhaust heat recovery heat exchanger 156 is configured by a part of the exhaust heat flow path 110 and a part of the second heat medium flow path 112, or in the exhaust heat flow path 110 or the second heat medium flow path 112. Has been placed. The exhaust heat recovery heat exchanger 156 is, for example, a double tube heat exchanger, a plate heat exchanger, a fin tube heat exchanger, or a shell tube heat exchanger.

  The second heat medium flow path 112 is configured to supply the second heat medium heated by the exhaust heat recovery heat exchanger 156 to a predetermined heat process. The thermal process means a process accompanied by a chemical change or a physical change due to heat. The predetermined thermal process varies depending on the application of the exhaust heat recovery apparatus 150A, but is, for example, phase change such as heating, combustion, evaporation, or desorption of an adsorbed substance. The heat recovery heat exchanger 156 can preheat the second heat medium to be supplied to a predetermined heat process.

  The condenser 154 is disposed upstream of the exhaust heat recovery heat exchanger 156 in the second heat medium flow path 112. For this reason, in the Rankine cycle 155, in the condenser 154, the working fluid expanded by the expander 153 and the second heat medium flow 112 flowing through the second heat medium flow path 112 before being heated by the exhaust heat recovery heat exchanger 156. The working fluid is condensed by exchanging heat with the medium. That is, the second heat medium flowing through the second heat medium flow path 112 is a low-temperature heat source of the Rankine cycle 155. The condenser 154 is, for example, a double tube heat exchanger, a fin tube heat exchanger, a plate heat exchanger, or a shell tube heat exchanger. The working fluid can be condensed by the second heat medium before being heated by the exhaust heat recovery heat exchanger 156. Further, the condenser 154 can preheat the second heat medium.

  The exhaust heat recovery heat exchanger 156 is disposed on the downstream side of the evaporator 152 in the exhaust heat flow path 110, and is disposed on the downstream side of the condenser 154 in the second heat medium flow path 112. That is, the exhaust heat recovery heat exchanger 156 exchanges heat with the first heat medium flowing through the exhaust heat flow path 110 after exchanging heat with the working fluid in the evaporator 152 and the first heat medium after exchanging heat with the working fluid in the condenser 154. Heat exchange is performed with the second heat medium flowing through the two heat medium flow paths 112.

  The operation of the exhaust heat recovery apparatus 150A will be described. When the temperature of the first heat medium flowing through the exhaust heat flow path 110 that exchanges heat with the working fluid in the evaporator 152 is, for example, in the range of 100 ° C. or higher and 150 ° C. or lower, the liquid phase enclosed in the Rankine cycle 155 The working fluid is sent to the evaporator 152 by the pump 151. In the evaporator 152, the exhaust heat of the first heat medium flowing through the exhaust heat flow path 110 is recovered, and the working fluid is evaporated by the exhaust heat. The pressure of the working fluid is high between the outlet of the pump 151 and the inlet of the expander 153 in the Rankine cycle 155 due to the increase in the vapor pressure accompanying the evaporation of the working fluid sent to the evaporator 152 by the work of the pump 151. At this time, the evaporator 152 is cooled by the evaporation of the working fluid, so that it is protected from the exhaust heat of the first heat medium.

  In the evaporator 152, heat exchange is performed between the first heat medium flowing through the exhaust heat flow path 110 and the working fluid. The first heat medium flows through the exhaust heat passage 110 from the upstream side toward the downstream side. In the evaporator 152, two fluids having a temperature difference are subjected to heat exchange, so that the temperature boundary layer on the surface of the heat exchanger constituting the evaporator 152 can be thinned. Since the heat transfer coefficient on the surface of the heat exchanger is large and the heat exchange efficiency of the evaporator 152 is high, the evaporator 152 can be downsized.

  In the condenser 154, the working fluid is cooled by heat exchange with the second heat medium flowing through the second heat medium flow path 112, so the working fluid is condensed. The working fluid pressure is low between the outlet of the expander 153 and the inlet of the pump 151 in the Rankine cycle 155. Accordingly, since the pressure of the working fluid on the evaporator 152 side of the expander 153 is high and the pressure of the working fluid on the condenser 154 side of the expander 153 is low, the vapor-phase working fluid heated and evaporated by the evaporator 152 Passes through the expander 153 and flows to the condenser 154. The expander 153 converts the energy that the working fluid flows into rotation power by a rotation mechanism. Thereby, Rankine cycle 155 generates motive power. The generator 170 is driven by this rotational power to generate power.

  The working fluid that has passed through the expander 153 is supplied to the condenser 154 and exchanges heat with the second heat medium flowing through the second heat medium flow path 112 to heat the second heat medium.

  The exhaust heat recovery heat exchanger 156 is disposed at a position downstream of the evaporator 152 in the exhaust heat flow path 110 and a position downstream of the condenser 154 in the second heat medium flow path 112. For this reason, the exhaust heat recovery heat exchanger 156 recovers the exhaust heat of the first heat medium flowing through the exhaust heat flow path 110 that has not been recovered in the Rankine cycle 155. The second heat medium flowing through the second heat medium flow path 112 is further heated by the recovered exhaust heat. For this reason, the exhaust heat which a 1st heat medium has can be utilized efficiently.

  The Rankine cycle 155 is configured such that the difference between the temperature of the high temperature heat source and the temperature of the low temperature heat source is in a range suitable for efficient operation of the Rankine cycle 155. Specifically, the evaporator 152 is disposed in the exhaust heat flow path 110 at a position where the temperature of the first heat medium passing through the evaporator 152 falls within an appropriate range. Further, the condenser 154 is disposed in the second heat medium flow path 112 at a position where the temperature of the second heat medium passing through the condenser 154 falls within an appropriate range. For this reason, the amount of exhaust heat recovered by the first heat medium in the evaporator 152 is limited. As a result, since the difference between the temperature of the high temperature heat source at the outlet of the evaporator 152 and the temperature of the low temperature heat source at the outlet of the condenser 154 is not too small, the efficiency of power generation by the Rankine cycle 155 is improved. The difference between the temperature of the high temperature heat source and the temperature of the low temperature heat source is large, and the exhaust heat of the first heat medium that can efficiently operate the Rankine cycle 155 is recovered by the evaporator 152 of the Rankine cycle 155. On the other hand, the exhaust heat of the first heat medium that is not suitable for the efficient operation of the Rankine cycle 155 is recovered by the exhaust heat recovery heat exchanger 156 because the difference between the temperature of the high temperature heat source and the temperature of the low temperature heat source is small.

  Rankine cycle 155 operates efficiently when exhaust heat recovery device 150A includes exhaust heat recovery heat exchanger 156. This is because the high-temperature first heat medium before being cooled by the exhaust heat recovery heat exchanger 156, the low-temperature second heat medium before being heated by the exhaust heat recovery heat exchanger 156, the working fluid of the Rankine cycle 155, This is because heat is exchanged. Thus, by sharing the recovery of the exhaust heat of the first heat medium by the evaporator 152 and the exhaust heat recovery heat exchanger 156 of the Rankine cycle 155, appropriate exhaust heat recovery can be performed in the evaporator 152 of the Rankine cycle 155. Done. Further, since the amount of exhaust heat recovered by the evaporator 152 of the Rankine cycle 155 can be reduced, the evaporator 152 can be reduced in size.

  Rankine cycle 155 exchanges heat between the first heat medium and the working fluid flowing through exhaust heat flow path 110 in evaporator 152. Thus, power generation can be performed using the Rankine cycle 155 and the generator 170. In the Rankine cycle 155, in the condenser 154, the working fluid expanded by the expander 153 and the second heat medium flowing through the second heat medium flow path 112 before being heated by the exhaust heat recovery heat exchanger 156 are provided. And heat exchange. Thereby, the second heat medium can be preheated. The exhaust heat recovery heat exchanger 156 exchanges heat between the first heat medium flowing through the exhaust heat flow path 110 and the second heat medium flowing through the second heat medium flow path 112. Thereby, the second heat medium can be preheated. For this reason, the exhaust heat recovery apparatus 150A can use the exhaust heat recovered from the first heat medium not only for power generation but also for other uses such as preheating of the second heat medium. For this reason, the exhaust heat which a 1st heat medium has can be utilized efficiently.

  Since the Rankine cycle 155 and the exhaust heat recovery heat exchanger 156 appropriately share the recovery of the exhaust heat of the first heat medium, the exhaust heat recovery apparatus 150A recovers from the first heat medium by the evaporator 152 of the Rankine cycle 155. The amount of exhaust heat is reduced. For this reason, the efficiency of power generation by Rankine cycle 155 is also increased. Further, the Rankine cycle 155 can be reduced in size, and the cost of the exhaust heat recovery apparatus 150A can be reduced.

  As long as the Rankine cycle 155 generates power, the exhaust heat recovery apparatus 150A may not include the generator 170. In this case, the power generated in the Rankine cycle 155 may be used to drive a machine other than the generator.

(First modification)
The exhaust heat recovery device 150A can be changed from various viewpoints. As shown in FIG. 2, the exhaust heat recovery device 150 </ b> A may be modified like an exhaust heat recovery device 150 </ b> B according to the first modification. The exhaust heat recovery device 150B is configured in the same manner as the exhaust heat recovery device 150A, unless otherwise specified. The same or corresponding components of the exhaust heat recovery device 150B as those of the exhaust heat recovery device 150A may be assigned the same reference numerals as the exhaust heat recovery device 150A, and detailed description thereof may be omitted. The description regarding the exhaust heat recovery device 150A is also applied to the exhaust heat recovery device 150B unless there is a technical contradiction. This also applies to other variations.

  The exhaust heat recovery heat exchanger 156 of the exhaust heat recovery apparatus 150B is disposed on the upstream side of the evaporator 152 in the exhaust heat flow path 110, and is disposed on the downstream side of the condenser 154 in the second heat medium flow path 112. Has been. That is, the exhaust heat recovery heat exchanger 156 exchanges heat with the first heat medium flowing through the exhaust heat flow path 110 before heat exchange with the working fluid in the evaporator 152 and the working fluid in the condenser 154. Heat exchange is performed with the second heat medium flowing through the two heat medium flow paths 112. When the temperature of the first heat medium flowing into the exhaust heat recovery device 150B is too high for the Rankine cycle 155, the first heat medium flowing through the exhaust heat flow path 110 is subjected to the first heat before exchanging heat with the working fluid in the evaporator 152. The temperature of the medium can be appropriately reduced. As a result, the temperature of the high-temperature heat source falls within a range where Rankine cycle 155 can operate efficiently.

  Similarly to the exhaust heat recovery device 150A, the exhaust heat recovery device 150B can use the exhaust heat recovered from the first heat medium not only for power generation but also for other uses such as preheating of the second heat medium. For this reason, the exhaust heat which a 1st heat medium has can be utilized efficiently. Further, the amount of exhaust heat recovered from the first heat medium by the evaporator 152 of the Rankine cycle 155 is reduced. For this reason, Rankine cycle 155 can be reduced in size and cost reduction of exhaust heat recovery device 150B can be achieved.

(Second modification)
As shown in FIG. 3, the exhaust heat recovery device 150 </ b> A may be modified like an exhaust heat recovery device 150 </ b> C according to the second modification. In the condenser 154, the Rankine cycle 155 of the exhaust heat recovery apparatus 150C condenses the working fluid by exchanging heat between the working fluid expanded by the expander 153 and a cooling medium different from the second heat medium. The exhaust heat recovery apparatus 150C includes a fan 157, for example. The fan 157 supplies air outside the exhaust heat recovery apparatus 150C toward the condenser 154 as a cooling medium. The exhaust heat recovery device 150C may be configured to supply seawater, river water, lake water, or the like as a cooling medium to the condenser 154 by a pump. Even when the temperature of the second heat medium flowing through the second heat medium flow path 112 is high and not suitable as the temperature of the low-temperature heat source of the Rankine cycle 155, the Rankine cycle 155 can be operated efficiently.

  The exhaust heat recovery heat exchanger 156 is disposed on the upstream side of the evaporator 152 in the exhaust heat channel 110 and is disposed on the downstream side of the condenser 154 in the second heat medium channel 112. That is, the exhaust heat recovery heat exchanger 156 has a first heat medium flowing through the exhaust heat flow path 110 before heat exchange with the working fluid in the evaporator 152 and a second heat medium flowing through the second heat medium flow path 112. Exchange heat with the heat medium.

  The exhaust heat recovery device 150C recovers the exhaust heat of the first heat medium when the temperature of the first heat medium is too high for the Rankine cycle 155 by the exhaust heat recovery heat exchanger 156, and heats the second heat medium. Accordingly, the temperature of the first heat medium is appropriately lowered before the first heat medium exchanges heat with the working fluid in the evaporator 152. The Rankine cycle 155 uses the first heat medium, which has become an appropriate temperature for the Rankine cycle 155 by the exhaust heat recovery heat exchanger 156, as a high-temperature heat source, and an inexhaustible cooling medium such as air outside the exhaust heat recovery apparatus 150C. Is used as a low-temperature heat source. Thus, power is generated by the Rankine cycle 155 and the generator 170. Power can be generated using the Rankine cycle 155 and the generator 170 by the exhaust heat of the first heat medium whose temperature has decreased due to the exhaust heat recovery by the exhaust heat recovery heat exchanger 156.

  Similarly to the exhaust heat recovery apparatus 150A, the exhaust heat recovery apparatus 150C can use the exhaust heat recovered from the first heat medium not only for power generation but also for other uses such as preheating of the second heat medium. For this reason, the exhaust heat which a 1st heat medium has can be utilized efficiently. Further, the amount of exhaust heat recovered from the first heat medium by the evaporator 152 of the Rankine cycle 155 is reduced. For this reason, the efficiency of power generation by Rankine cycle 155 is also increased. Further, the Rankine cycle 155 can be reduced in size, and the cost of the exhaust heat recovery apparatus 150C can be reduced.

(Third Modification)
As shown in FIG. 4, the exhaust heat recovery device 150 </ b> A may be modified like an exhaust heat recovery device 150 </ b> D according to the third modification. In the condenser 154, the Rankine cycle 155 of the exhaust heat recovery device 150D performs heat exchange between the working fluid expanded by the expander 153 and a cooling medium different from the second heat medium in the condenser 154. The working fluid is condensed. Further, the exhaust heat recovery heat exchanger 156 is disposed upstream of the evaporator 152 in the exhaust heat flow path 110 and is disposed downstream of the condenser 154 in the second heat medium flow path 112. That is, the exhaust heat recovery heat exchanger 156 has a first heat medium flowing through the exhaust heat flow path 110 before heat exchange with the working fluid in the evaporator 152 and a second heat medium flowing through the second heat medium flow path 112. Exchange heat with the heat medium. The exhaust heat recovery device 150D is configured in the same manner as the exhaust heat recovery device 150C except that the positional relationship between the evaporator 152 and the exhaust heat recovery heat exchanger 156 is reversed in the exhaust heat flow path 110.

  The exhaust heat recovery apparatus 150 </ b> D can first recover the exhaust heat of the first heat medium flowing into the exhaust heat recovery apparatus 150 </ b> D at an appropriate temperature as the high temperature heat source of the Rankine cycle 155 with the evaporator 152 of the Rankine cycle 155. Further, the exhaust heat of the first heat medium that has not been recovered by the evaporator 152 can be recovered by the exhaust heat recovery heat exchanger 156. For this reason, similarly to the exhaust heat recovery apparatus 150A, the Rankine cycle 155 and the exhaust heat recovery heat exchanger 156 can appropriately share the recovery of the exhaust heat of the first heat medium. Even when the temperature of the second heat medium flowing through the second heat medium flow path 112 is high and not suitable as the temperature of the low-temperature heat source of the Rankine cycle 155, the Rankine cycle 155 can be operated efficiently.

<Heating system>
Next, the heating system 100 provided with said waste heat recovery apparatus is demonstrated. As shown in FIG. 5, the heating system 100 includes a furnace body 101, a combustion unit 105, a heating space 102, an exhaust passage 120, an intake passage 130, a reheat passage 107, a heating passage 108, an exhaust heat recovery device 150A, And a transfer device 104.

  The combustion unit 105 includes a burner 105A. The intake passage 130 is a passage for supplying outside air to the combustion unit 105. An intake fan 111 is provided in the intake passage 130. The outside air is supplied to the combustion unit 105 by the operation of the intake fan 111. Thereby, the combustion part 105 burns fuel with the burner 105A, and generates heat.

  The heating space 102 is connected to the combustion unit 105 by a heating channel 108. The object to be heated 103 is conveyed to the heating space 102 by the conveying device 104. The heating space 102 is a space for heating the article to be heated 103 using the heat generated in the combustion unit 105. The heated object 103 is heated by the transfer device 104 to the outside of the heating space 102.

  Since the combustion gas generated in the combustion section 105 is continuously supplied to the heating space 102 through the heating flow path 108, exhaust gas is generated in the heating space 102. The exhaust channel 120 is a channel for exhausting the exhaust gas generated in the heating space 102. The discharge channel 120 is connected to the heating space 102. An exhaust fan 109 is disposed in the middle of the discharge channel 120. By operating the exhaust fan 109, the exhaust gas generated in the heating space 102 is discharged to the outside of the heating system 100. The exhaust heat flow path 110 of the exhaust heat recovery apparatus 150A is connected to the exhaust flow path 120 so that the exhaust gas is supplied to the exhaust heat flow path 110 as the first heat medium.

  In the second heat medium flow path 112 (see FIG. 1) of the exhaust heat recovery apparatus 150A, the outside air supplied to the combustion section 105 is supplied to the combustion section 105 as the second heat medium via the second heat medium flow path 112. As described above, at least a part of the intake flow path 130 is formed.

  The reheat channel 107 is a channel for supplying part of the air in the heating space 102 to the combustion unit 105. The reheat channel 107 is connected to the heating space 102. A circulation fan 106 is provided in the middle of the reheat channel 107. When the circulation fan 106 operates, a part of the air in the heating space 102 flows through the reheat channel 107 and is supplied to the combustion unit 105. The reheat channel 107 is connected to the intake channel 130 in the middle of the intake channel 130. For this reason, the outside air flowing through the intake passage 130 and the air flowing through the reheat passage 107 are mixed and supplied to the combustion unit 105. Note that the reheat channel 107 may be directly connected to the combustion unit 105 without being connected to the intake channel 130.

  The operation of the heating system 100 will be described. First, the intake fan 111, the exhaust fan 109, and the circulation fan 106 are operated to generate an air flow inside the heating system 100. Next, fuel is supplied to the burner 105A, and the burner 105A is ignited. By supplying air, which is a mixture of outside air flowing through the intake flow path 130 and air flowing through the reheat flow path 107, to the combustion unit 105, fuel burns in the burner 105A. Thereby, combustion gas is generated. Further, the air in the combustion section 105 that is not directly involved in the fuel combustion in the burner 105A is heated by the combustion gas. The combustion gas and air heated by the combustion gas are supplied to the heating space 102 through the heating flow path 108. Exhaust gas is exhausted from the heating space 102 through the exhaust flow path 120 at a flow rate similar to the flow rate of outside air supplied to the combustion unit 105 through the intake flow path 130.

  After the temperature of the air in the heating space 102 reaches a predetermined temperature, the article to be heated 103 is transferred to the heating space 102 by the transfer device 104. When the object to be heated 103 is heated in the heating space 102, processing for the object to be heated 103 such as drying, curing of the paint in baking coating, and brazing is performed.

  The exhaust heat recovery apparatus 150A operates as described above, using the exhaust gas discharged from the heating space 102 as the first heat medium, and using the outside air flowing through the intake passage 130 as the second heat medium. As a result, the exhaust heat recovery device 150 </ b> A performs power generation by the Rankine cycle 155 and the generator 170 and preheats the outside air to be supplied to the combustion unit 105.

  The generated electric power is used, for example, for the operation of the conveying device 104, the circulation fan 106, the exhaust fan 109, or the intake fan 111 that consumes electric power in the heating system 100. Thereby, the electric power which should be supplied with respect to the heating system 100 from the outside can be reduced. Further, since the outside air supplied to the combustion unit 105 is preheated by the exhaust heat recovery device 150A, the amount of heat to be generated by the combustion of fuel in the burner 105A can be reduced. This saves fuel. As a result, the heating system 100 has high energy saving performance. The generated electric power may be supplied to the outside of the heating system 100.

  The heating system 100 may include an exhaust heat recovery device 150B, an exhaust heat recovery device 150C, or an exhaust heat recovery device 150D instead of the exhaust heat recovery device 150A. Further, in the heating system 100, the reheat channel 107 and the circulation fan 106 may be omitted.

<Steam boiler>
Next, the steam boiler 200 provided with said waste heat recovery apparatus is demonstrated. As shown in FIG. 6, the steam boiler 200 includes a combustor 205, a combustion gas channel 207, a steam generator 202, a liquid supply channel 250, a steam channel 260, and an exhaust heat recovery device 150A. The combustor 205 burns fuel to generate combustion gas. The combustion gas flows through the combustion gas passage 207. The steam generator 202 evaporates the liquid by exchanging heat between the combustion gas generated in the combustor 205 and the liquid. The liquid evaporated in the steam generator 202 is, for example, water. The steam generator 202 is, for example, a finned tube heat exchanger or a bare tube heat exchanger. The liquid supply channel 250 is a channel for supplying a liquid to the steam generator 202. The liquid supply flow path 250 is connected to the steam generator 202. The steam channel 260 supplies the steam generated by the steam generator 202 to the outside of the steam boiler 200.

  The exhaust heat flow path 110 of the exhaust heat recovery apparatus 150A is configured such that the combustion gas after heat exchange with the liquid in the steam generator 202 flows through the exhaust heat flow path 110 as the first heat medium. Specifically, the exhaust heat passage 110 is formed by a portion of the combustion gas passage 207 on the downstream side of the steam generator 202. In the second heat medium flow path 112 of the exhaust heat recovery apparatus 150A, the liquid to be supplied to the steam generator 202 is supplied to the steam generator 202 as the second heat medium via the second heat medium flow path 112. Thus, at least a part of the liquid supply flow path 250 is formed.

  The operation of the steam boiler 200 will be described. First, a pump (not shown) is operated to supply liquid to the steam generator 202 through the liquid supply channel 250. Next, fuel is supplied to the combustor 205 and the combustor 205 is ignited. Combustion gas generated by the combustion of fuel in the combustor 205 flows through the combustion gas passage 207. In the steam generator 202, the combustion gas 207 exchanges heat with the liquid inside the steam generator 202. Thereby, the steam generator 202 evaporates the liquid. The steam generated by the steam generator 202 is supplied to the outside of the steam boiler 200 through the steam channel 260.

  The exhaust heat recovery device 150A uses the combustion gas after heat exchange with the liquid in the steam generator 202 as the first heat medium, and uses the liquid to be supplied to the steam generator 202 as the second heat medium as described above. Operate. Accordingly, the exhaust heat recovery device 150A performs power generation by the Rankine cycle 155 and the generator 170 and preheating of the liquid to be supplied to the steam generator 202.

  The generated electric power is used, for example, to operate a device that consumes electric power in a steam boiler 200 such as a pump for flowing a liquid through the liquid supply passage 250 or a blower (not shown). Thereby, the electric power which should be supplied with respect to the steam boiler 200 from the outside can be reduced. Further, since the liquid to be supplied to the steam generator 202 is preheated by the exhaust heat recovery device 150A, the amount of heat to be generated by the combustion of fuel in the combustor 205 can be reduced. This saves fuel. As a result, the steam boiler 200 has high energy saving performance. The generated electric power may be supplied to the outside of the steam boiler 200.

<Deodorization system>
Next, the deodorizing system 300A provided with the above exhaust heat recovery apparatus will be described. As shown in FIG. 7, the deodorization system 300A includes a combustion unit 360, an exhaust channel 310, a supply channel 320, a process fluid channel 350, an exhaust heat recovery device 150B, a concentration unit 340, and an introduction channel 370. The combustion unit 360 burns odorous substances. Thereby, the odor substance is decomposed. An odorous substance is an organic compound contained in the gas discharged | emitted from the production process in a factory, for example. The concentrating unit 340 concentrates the odorous substance, and the concentrated odorous substance is supplied to the combustion unit 360. Exhaust gas is generated by burning odorous substances in the combustion unit 360. The exhaust flow path 310 is a flow path for discharging exhaust gas generated by burning odorous substances in the combustion unit 360.

  The process fluid channel 350 is a channel for supplying a process fluid to a predetermined thermal process. The process fluid is, for example, air sucked from the outside of the deodorizing system 300A. The process fluid flow path 350 is connected to the concentration unit 340, and the process fluid is supplied to the concentration unit 340.

  The exhaust heat flow path 110 of the exhaust heat recovery apparatus 150B is connected to the exhaust flow path 310 so that the exhaust gas generated in the combustion unit 360 is supplied to the exhaust heat flow path 110 as the first heat medium. Further, the second heat medium flow path 112 of the exhaust heat recovery apparatus 150B has a process fluid flow so that the process fluid is supplied as a second heat medium to the predetermined heat process via the second heat medium flow path 112. At least a part of the path 350 is formed.

  The combustion unit 360 includes a preheating unit 360A and a catalyst combustion unit 360B. The preheating unit 360A preheats the odor substance. The preheating unit 360 </ b> A has a burner 305. The odorous substance is preheated by the heat generated by burning the fuel in the burner 305. The catalyst combustion unit 360B has a catalyst. The catalyst is, for example, a metal such as platinum, palladium, ruthenium, rhodium, silver, or a nitrate or chloride thereof. The catalyst is supported on a structure such as a metal honeycomb, a ceramic honeycomb, or a ball pellet in the catalyst combustion unit 360B. The catalytic combustion unit 360B causes the preheated odorous substance to come into contact with the catalyst to perform catalytic combustion.

  After the odorous substance is adsorbed on the adsorbent, the concentrating unit 340 concentrates the odorous substance by desorbing the odorous substance from the adsorbent. The supply channel 320 connects the concentration unit 340 and the combustion unit 360, and is a channel for supplying the odorous substance concentrated in the concentration unit 340 to the combustion unit 360. The concentration unit 340 includes, for example, an annular concentration rotor (not shown) formed of an adsorbent. The adsorbent is, for example, zeolite. The concentration rotor is rotatably provided in the concentration unit 340. The concentrating unit 340 includes an adsorption region 341 and a regeneration region 342. The concentration rotor rotates so that a part of the concentration rotor alternately passes through the adsorption region 341 and the regeneration region 342. An introduction channel 370 is connected to the adsorption region 341. An odorous substance is supplied to the adsorption region 341 through the introduction flow path 370. In the adsorption region 341, the odorous substance is adsorbed by the adsorbent, that is, the concentration rotor.

  A process fluid flow path 350 is connected to the regeneration region 342. Process fluid is supplied to the regeneration region 342 through the process fluid flow path 350. Since the process fluid passes through the second heat medium flow path 112 of the exhaust heat recovery device 150B, it is preheated by the exhaust heat recovery device 150B. Accordingly, in the regeneration region 342, the adsorbent on which the odorous substance is adsorbed is heated by the process fluid that has passed through the second heat medium flow path 112 of the exhaust heat recovery apparatus 150B, and the odorous substance is desorbed from the adsorbent. That is, this process corresponds to a predetermined thermal process.

  The operation of the deodorizing system 300A will be described. First, the deodorization system 300A operates, for example, a fan (not shown) provided in the process fluid flow path 350, and the air outside the deodorization system 300A is supplied as a process fluid through the process fluid flow path 350 to the concentration unit 340. This is supplied to the reproduction area 342. Next, fuel is supplied to the burner 305 and the burner 305 is ignited. The concentration rotor of the concentration unit 340 is rotated. The odorous substance is supplied to the concentration unit 340 through the introduction channel 370, and the odorous substance is concentrated in the concentration unit 340. The odor substance concentrated in the concentration unit 340 is supplied to the preheating unit 360A through the supply channel 320 and preheated by the burner 305. The preheated odorous substance is catalytically burned by the catalytic combustion unit 360B, decomposed, and deodorized. Exhaust gas generated by burning odorous substances is supplied to the exhaust heat recovery device 150B through the exhaust passage 310.

  The exhaust heat recovery device 150B uses, as a first heat medium, the exhaust gas generated by burning the odorous substance in the combustion unit 360 supplied through the exhaust passage 310, and the process fluid flowing through the process fluid passage 350 is the second. It operates as described above using it as a heat medium. As a result, the exhaust heat recovery apparatus 150B performs power generation by the Rankine cycle 155 and the generator 170 and preheats the process fluid to be supplied to the regeneration region 342 of the concentration unit 340.

  The generated electric power is used, for example, to operate a device that consumes electric power in the deodorizing system 300A such as an adsorbent rotor and a fan of the concentrating unit 340. Thereby, the electric power which should be supplied from the exterior with respect to 300 A of deodorizing systems can be reduced. Moreover, since the process fluid is preheated by the exhaust heat recovery device 150A, the amount of heat for preheating the process fluid supplied to the concentrating unit 340 can be reduced. Thereby, the fuel consumed by the deodorizing system 300A can be saved. As a result, the deodorizing system 300A has high energy saving performance. The generated electric power may be supplied to the outside of the deodorizing system 300A.

(Modification)
Various changes can be made to the deodorizing system 300A. For example, the deodorization system 300A may be changed like a deodorization system 300B shown in FIG. The deodorization system 300A is configured in the same manner as the deodorization system 300A except that an exhaust heat recovery device 150C is used instead of the exhaust heat recovery device 150B. Even with such a configuration, the same effect as the deodorizing system 300A can be obtained.

  In the deodorization system 300 </ b> A, the predetermined thermal process is not limited to the thermal process in the concentration unit 340. For example, the predetermined thermal process may be combustion of odorous substances in the combustion unit 360. That is, the preheated process fluid may be supplied to the combustion unit 360 and used as combustion air. Further, the concentration unit 340 may be omitted. The combustion unit 360 may not be configured in accordance with a method for catalytically burning odorous substances, and may be configured in accordance with a direct combustion method in which odorous substances are directly burned by a burner, for example. The deodorization system 300B may be similarly changed. Furthermore, the deodorization system 300A may be changed so that the exhaust heat recovery device 150A or the exhaust heat recovery device 150D is used instead of the exhaust heat recovery device 150B.

DESCRIPTION OF SYMBOLS 100 Heating system 102 Heating space 105 Combustion part 107 Reheating flow path 110 Exhaust heat flow path 112 2nd heat medium flow path 120 Exhaust flow path 130 Intake flow path 150A-150D Waste heat recovery apparatus 151 Pump 152 Evaporator 153 Expander 154 Condenser 155 Rankine cycle 156 Waste heat recovery heat exchanger 170 Generator 200 Steam boiler 202 Steam generator 205 Combustor 250 Supply channel 300A, 300B Deodorization system 310 Exhaust channel 320 Supply channel 340 Concentrator 350 Process fluid channel 360 Combustion part 360A Preheating part 360B Catalytic combustion part

Claims (10)

An exhaust heat passage for flowing a first heat medium having exhaust heat;
A second heat medium flow path for flowing a second heat medium having a temperature lower than the temperature of the first heat medium;
A pump, an evaporator, an expander, and a condenser, wherein the working fluid is evaporated and evaporated by exchanging heat between the first heat medium flowing through the exhaust heat flow path and the working fluid in the evaporator. A Rankine cycle in which the working fluid is expanded by the expander to generate power;
The first heat medium is heated by exchanging heat between the first heat medium flowing through the exhaust heat flow path and the second heat medium flowing through the second heat medium flow path, thereby the first heat medium. e Bei and a heat recovery heat exchanger for recovering waste heat with the medium,
In the Rankine cycle, in the condenser, the working fluid expanded by the expander and the second heat medium flowing through the second heat medium flow path before being heated by the exhaust heat recovery heat exchanger And the heat exchange to condense the working fluid,
The exhaust heat recovery heat exchanger includes the first heat medium flowing through the exhaust heat flow path after exchanging heat with the working fluid in the evaporator, and the first heat medium flowing through the second heat medium flow path. 2 heat exchange with heat medium,
Waste heat recovery device.   The exhaust heat recovery apparatus according to claim 1, wherein the second heat medium flow path is configured to supply the second heat medium heated by the exhaust heat recovery heat exchanger to a predetermined heat process. .   The exhaust heat recovery apparatus according to claim 1, further comprising a generator that generates electric power by the power. The exhaust heat recovery heat exchanger is configured to exchange heat with the working fluid in the condenser and the first heat medium flowing through the exhaust heat passage after exchanging heat with the working fluid in the evaporator. The exhaust heat recovery apparatus according to any one of claims 1 to 3 , wherein heat exchange is performed between the second heat medium flowing through the second heat medium flow path. A combustion section;
A heating space for heating an object to be heated using heat generated in the combustion section;
A discharge passage for discharging the exhaust gas generated in the heating space;
An intake passage for supplying outside air to the combustion section;
An exhaust heat recovery device according to any one of claims 1 to 4 ,
The exhaust heat channel is connected to the exhaust channel so that the exhaust gas is supplied to the exhaust heat channel as the first heat medium,
The second heat medium flow path forms at least a part of the intake flow path so that the outside air is supplied as the second heat medium to the combustion unit via the second heat medium flow path. Yes,
Heating system. The heating system according to claim 5 , further comprising a reheat channel for supplying a part of air in the heating space to the combustion unit. A combustor,
A steam generator for evaporating the liquid by exchanging heat between the combustion gas generated in the combustor and the liquid;
A liquid supply passage for supplying the liquid to the steam generator;
An exhaust heat recovery device according to any one of claims 1 to 4 ,
The exhaust heat flow path is configured such that the combustion gas after heat exchange with the liquid in the steam generator flows through the exhaust heat flow path as the first heat medium,
The second heat medium flow path is configured such that the liquid to be supplied to the steam generator is supplied to the steam generator as the second heat medium via the second heat medium flow path. Forming at least part of the liquid supply flow path,
Steam boiler. A combustion section for burning odorous substances;
An exhaust passage for discharging exhaust gas generated by burning the odorous substance in the combustion section;
A process fluid flow path for supplying a process fluid to a predetermined thermal process;
An exhaust heat recovery device according to any one of claims 1 to 4 ,
The exhaust heat passage is connected to the exhaust passage so that the exhaust gas is supplied to the exhaust heat passage as the first heat medium,
The second heat medium flow path includes at least one of the process fluid flow paths so that the process fluid is supplied as the second heat medium to the predetermined heat process via the second heat medium flow path. Forming part,
Deodorization system. The deodorization system according to claim 8 , wherein the combustion unit includes a preheating unit that preheats the odorous substance, and a catalyst combustion unit that causes the preheated odorous substance to come into contact with a catalyst to perform catalytic combustion. A concentrating part for desorbing the odorous substance from the adsorbent and concentrating the odorous substance after adsorbing the odorous substance to the adsorbent;
A supply flow path for supplying the odorous substance concentrated in the concentration unit to the combustion unit,
Examples predetermined heat process, wherein the odorant by the process fluid that has passed through the second heat medium passage and heating the adsorbent having adsorbed desorbing the odorous substances from the adsorbent according to claim 8 or 9 Deodorizing system as described in.

Images